WO2020136815A1 - Séparateur d'huile, compresseur à vis et dispositif à cycle frigorifique - Google Patents

Séparateur d'huile, compresseur à vis et dispositif à cycle frigorifique Download PDF

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Publication number
WO2020136815A1
WO2020136815A1 PCT/JP2018/048176 JP2018048176W WO2020136815A1 WO 2020136815 A1 WO2020136815 A1 WO 2020136815A1 JP 2018048176 W JP2018048176 W JP 2018048176W WO 2020136815 A1 WO2020136815 A1 WO 2020136815A1
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WO
WIPO (PCT)
Prior art keywords
oil
outer cylinder
oil separator
return hole
screw compressor
Prior art date
Application number
PCT/JP2018/048176
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English (en)
Japanese (ja)
Inventor
直人 上中居
Original Assignee
三菱電機株式会社
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Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2018/048176 priority Critical patent/WO2020136815A1/fr
Publication of WO2020136815A1 publication Critical patent/WO2020136815A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B39/00—Component parts, details, or accessories, of pumps or pumping systems specially adapted for elastic fluids, not otherwise provided for in, or of interest apart from, groups F04B25/00 - F04B37/00
    • F04B39/04—Measures to avoid lubricant contaminating the pumped fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/02—Lubrication; Lubricant separation

Definitions

  • the present invention relates to an oil separator for separating refrigerating machine oil from a refrigerant, a screw compressor equipped with the oil separator, and a refrigeration cycle apparatus equipped with the screw compressor.
  • the refrigerating machine oil when the refrigerating machine oil is discharged from the screw compressor and the refrigerating machine oil flows into the range on the downstream side of the screw compressor in the refrigeration cycle circuit, it adversely affects the heat exchange in the condenser and the evaporator. However, it may cause a decrease in performance. Therefore, before the refrigerating machine oil flows into the refrigerating cycle circuit, it is necessary to separate the refrigerant gas and the refrigerating machine oil with an oil separator and recover the refrigerating machine oil.
  • a conventional screw compressor that includes an oil separator that separates refrigerating machine oil from the refrigerant gas discharged from the compression chamber (see Patent Document 1).
  • an oil separator that separates refrigerating machine oil from the refrigerant gas discharged from the compression chamber
  • Patent Document 1 As a method for separating the refrigerating machine oil and the refrigerant gas, there is a method called a cyclone method for separating the refrigerating machine oil and the refrigerant gas by a centrifugal force by utilizing a difference in gas-liquid density.
  • Cyclone type oil separator includes an oil separation unit and an oil storage unit.
  • the oil separation section includes a centrifugal separation section and a passage section.
  • the centrifugal separation portion is formed of a double cylinder and generates a centrifugal force for separating oil between the outer cylinder part and the inner cylinder part.
  • the passage portion swirls and raises the refrigerant gas, which is separated from the refrigerating machine oil by centrifugal force and descends while swirling, to the inner side of the inner cylindrical portion.
  • the refrigerant that has flowed into the inner tubular portion flows out of the oil separator, in other words, flows out of the screw compressor, and flows into a range on the downstream side of the screw compressor in the refrigeration cycle circuit.
  • the oil storage section stores the separated refrigerating machine oil.
  • the conventional cyclone type oil separator In the conventional cyclone type oil separator, a part of the refrigerant gas flowing as a swirl flow in the oil separation section flows into the oil storage section as a swirl flow. Then, the swirling flow flowing into the oil storage portion roughens the oil level of the refrigeration oil stored in the oil storage portion. Therefore, for example, when the oil level of the refrigerating machine oil stored in the oil storage section is high, the refrigerating machine oil that has jumped due to the rough oil level returns to the oil separation section and is wound up in a swirling flow. Will flow out of the screw compressor. That is, in the refrigeration cycle circuit, the refrigerating machine oil flows out into a range on the downstream side of the screw compressor. As described above, the conventional cyclone type oil separator has a problem that the oil separation performance may be deteriorated due to the swirling flow entering the oil reservoir from the oil separator.
  • the present invention is intended to solve the above problems, and a first object of the present invention is to provide an oil separator having an oil separation efficiency higher than that of the related art.
  • a second object of the present invention is to provide a screw compressor equipped with such an oil separator, and a refrigeration cycle apparatus equipped with the screw compressor.
  • the oil separator according to the present invention includes a tubular outer tubular portion in which a refrigerant gas inlet is formed, and a tubular inner tubular portion provided inside the outer tubular portion at a position facing the inlet. And an oil storage part provided below the outer cylinder part for storing refrigerating machine oil, and a partition plate for partitioning the outer cylinder part and the oil storage part, and the inside of the outer cylinder part and the oil. An oil return hole communicating with the reservoir is formed, and a current plate is provided in the oil return hole.
  • the screw compressor according to the present invention includes the oil separator according to the present invention, and a screw rotor having a spiral groove formed on the outer peripheral portion, which serves as a compression chamber for compressing the refrigerant gas.
  • the refrigeration cycle apparatus includes the screw compressor according to the present invention, a condenser, an expansion valve, and an evaporator.
  • the oil separator according to the present invention a swirling flow of the refrigerant gas is generated inside the outer cylinder portion, and the refrigerant gas and the refrigerating machine oil are separated.
  • the oil separator according to the present invention when the swirling flow inside the outer tubular portion enters the oil reservoir through the oil return hole, it is rectified by the flow straightening plate provided in the oil return hole. Therefore, the oil separator according to the present invention can suppress the oil level of the refrigerating machine oil stored in the oil storage portion from becoming rough compared to the conventional oil separator. Therefore, the oil separator according to the present invention has improved oil separation efficiency as compared with the related art.
  • FIG. 2 is a cross-sectional view of the oil separator of the screw compressor according to the first embodiment of the present invention, taken along the line AA in FIG. 1. It is a cross-sectional view which shows another example of the oil separator of the screw compressor which concerns on Embodiment 1 of this invention. It is a refrigerant circuit diagram which shows the refrigerating cycle device in Embodiment 2 of this invention.
  • FIG. 1 is a vertical cross-sectional view showing a screw compressor according to Embodiment 1 of the present invention.
  • the screw compressor 1 includes a compressor body 2 on the C side on the right side of the chain double-dashed line S.
  • the screw compressor 1 includes an oil separator 3 on the O side on the left side of the two-dot chain line S.
  • the screw compressor 1 is a single screw compressor equipped with an oil separator 3.
  • the screw compressor 1 includes a compressor body 2 and an oil separator 3.
  • the oil separator 3 is fastened by a bolt to a casing 4 that forms the outer shell of the compressor body 2.
  • the compressor body 2 includes a casing 4, a motor 5, a drive shaft 6, a screw rotor 7, and a bearing 8.
  • the casing 4 is formed in a tubular shape and constitutes the outer shell of the compressor body 2 as described above.
  • the motor 5 is housed in the casing 4.
  • the drive shaft 6 is fixed to the motor 5 and is rotationally driven by the motor 5.
  • the screw rotor 7 is fixed to the drive shaft 6.
  • the bearing 8 rotatably supports the end of the drive shaft 6 that is not fixed to the motor 5.
  • the compressor body 2 includes a pair of gate rotors 9.
  • the pair of gate rotors 9 are arranged so as to be axially symmetric with respect to the drive shaft 6 at positions facing the outer peripheral portion of the screw rotor 7.
  • the compressor body 2 includes a slide valve 10 which is slidable between an inner peripheral surface of the casing 4 and the screw rotor 7 along the outer peripheral surface of the screw rotor 7 on the suction pressure side and the discharge pressure side.
  • the slide valve 10 has an opening 10a at the center.
  • the motor 5 includes a stator 5a fixed to the inner peripheral surface of the casing 4 and a rotor 5b arranged inside the stator 5a.
  • the rotor 5b is fixed to the drive shaft 6. Further, the central axis of the drive shaft 6 and the central axis of the screw rotor 7 are arranged on the same line.
  • the screw rotor 7 is formed in a cylindrical shape. On the outer peripheral portion of the screw rotor 7, for example, a plurality of spiral grooves 7a are formed from one end to the other end of the screw rotor 7. As described later, the groove 7a serves as the compression chamber 11 that compresses the refrigerant.
  • the casing 4 is separated into a suction pressure side filled with a low-pressure refrigerant gas and a discharge pressure side filled with a high-pressure refrigerant gas.
  • One end side of the screw rotor 7 serves as a suction side of the refrigerant gas and connects the groove 7a with the suction pressure side.
  • the other end side of the screw rotor 7 serves as a refrigerant gas discharge side, and connects the groove 7a with the discharge pressure side.
  • the gate rotor 9 is formed in a disc shape.
  • a plurality of tooth portions 9a are provided on the outer peripheral portion of the gate rotor 9 along the circumferential direction.
  • the tooth portion 9a of the gate rotor 9 is arranged so as to mesh with the groove 7a of the screw rotor 7.
  • a space surrounded by the groove 7a, the tooth portion 9a of the gate rotor 9, the inner peripheral surface of the casing 4, and the slide valve 10 serves as a compression chamber 11 filled with a refrigerant gas to be compressed. Refrigerating machine oil for sealing the compression chamber 11 is injected into the compression chamber 11.
  • a discharge port (not shown) connected to the discharge chamber 12 is opened on the inner peripheral surface of the casing 4 on the discharge pressure side.
  • the high-pressure refrigerant gas and the refrigerating machine oil filled in the compression chamber 11 are discharged into the discharge chamber 12 through the opening 10a of the slide valve 10 and the discharge port.
  • the discharge chamber 12 is a space in which the high-pressure refrigerant gas and the refrigerating machine oil in the compression chamber 11 are discharged.
  • the high-pressure refrigerant gas and refrigerating machine oil filled in the discharge chamber 12 flow into the oil separator 3.
  • the oil separator 3 is a cyclone type oil separator for separating refrigerant gas and refrigerating machine oil.
  • the oil separator 3 is fastened to the casing 4 of the compressor body 2 with bolts.
  • the oil separator 3 is formed in a double-cylindrical shape and includes a cylindrical outer cylinder portion 13 and a cylindrical inner cylinder portion 14.
  • An inlet 20 for the refrigerant gas is formed in the outer cylinder portion 13.
  • the inflow port 20 communicates with the discharge chamber 12 of the compressor body 2. That is, the refrigerant gas and the refrigerating machine oil flowing out from the compressor body 2 flow into the outer cylinder portion 13 from the inflow port 20. Then, the inside of the outer cylinder portion 13 becomes an oil separation space 16 for separating the refrigerant gas and the refrigerating machine oil.
  • the inner tubular portion 14 is provided inside the outer tubular portion 13 at a position facing the inflow port 20.
  • the inflow port 20 is arranged at a position higher than the lower end of the inner tubular portion 14 and lower than the upper end of the inner tubular portion 14. That is, the refrigerant gas and the refrigerating machine oil flowing from the inflow port 20 into the outer cylinder portion 13 flow between the outer cylinder portion 13 and the inner cylinder portion 14.
  • the outer cylinder portion 13 and the inner cylinder portion 14 are concentric cylinders having the same central axis.
  • the lower end of the inner tubular portion 14 is arranged above the lower end of the outer tubular portion 13.
  • the oil separator 3 includes a lid 15 that covers the upper opening of the outer tubular portion 13 and the upper opening of the inner tubular portion 14.
  • the inner cylinder portion 14 is fixed to the lid portion 15.
  • the outer cylinder part 13, the inner cylinder part 14, and the lid part 15 constitute an oil separation part 17 of the oil separator 3.
  • the oil separator 3 includes an oil storage portion 19 below the oil separation portion 17, in other words, below the outer cylinder portion 13, which stores refrigerating machine oil separated from the refrigerant gas.
  • the oil reservoir 19 communicates with the compressor body 2.
  • the oil storage portion 19 is formed wider than the downward projection area of the oil separation portion 17 and long on the compressor body 2 side.
  • the oil separator 3 includes a partition plate 51 that partitions the outer cylinder portion 13 and the oil storage portion 19. That is, the partition plate 51 partitions the oil separating section 17 and the oil storage section 19.
  • the partition plate 51 covers the lower opening of the outer tubular portion 13. Further, the partition plate 51 is arranged in parallel with the annular edge of the lower opening of the inner tubular portion 14.
  • the partition plate 51 and the outer cylinder portion 13 are integrally molded.
  • the method of integrally forming the partition plate 51 and the outer cylinder portion 13 is not particularly limited, such as a method of joining the partition plate 51 and the outer cylinder portion 13 by welding.
  • the partition plate 51 and the outer cylinder portion 13 are integrally molded by casting.
  • the lid portion 15 of the oil separating portion 17 is formed in a disc shape.
  • a through hole having a smaller diameter than the inner diameter of the inner tubular portion 14 is formed in the center of the lid portion 15 so as to vertically penetrate the lid portion 15.
  • the through hole is an outlet portion 15 a that discharges the refrigerant gas after separating the refrigerating machine oil in the oil separator 3 to the outside of the oil separator 3.
  • the through hole is the outlet 15a for discharging the refrigerant gas after separating the refrigerating machine oil in the oil separator 3 to the outside of the screw compressor 1.
  • a check valve 18 is provided on the downstream side of the refrigerant gas flow at the outlet portion 15a. The check valve 18 may be built in the lid 15.
  • the oil separator 3 is provided with an oil return hole 50 that communicates the inside of the outer tubular portion 13 with the oil storage portion 19.
  • the oil return hole 50 is formed on the side surface of the outer tubular portion 13. More specifically, the oil return hole 50 is formed on the side surface of the outer tubular portion 13 on the side of the compressor body 2 in a size within a half circumferential region of the outer tubular portion 13. Further, the oil return hole 50 is formed up to the lower end of the outer tubular portion 13. Further, the upper end of the oil return hole 50 is arranged at a position lower than the lower end of the inner tubular portion 14.
  • the upper end of the oil return hole 50 is arranged at a position lower than the intermediate position between the lower end of the inner tubular portion 14 and the lower end of the outer tubular portion 13 in the vertical direction.
  • the oil return hole 50 may be formed in the partition plate 51.
  • FIG. 2 is a cross-sectional view of the oil separator of the screw compressor according to the first embodiment of the present invention taken along the line AA in FIG.
  • a current plate 52 is provided in the oil return hole 50 of the oil separator 3.
  • the current plate 52 extends in a direction substantially perpendicular to the flow passage cross section of the oil return hole 50 and in an up-down direction, and has, for example, a rectangular shape in a side view.
  • the oil return hole 50 is provided with a single flow straightening plate 52.
  • the straightening vane 52 is arranged substantially in the center of the oil return hole 50 in a plan view.
  • the end portion of the straightening vane 52 is in contact with the peripheral portion of the oil return hole 50.
  • the oil return hole 50 is formed on the side surface of the outer tubular portion 13. Then, the oil return hole 50 is formed up to the lower end of the outer tubular portion 13. Therefore, the lower end of the flow regulating plate 52 is in contact with the partition plate 51 that constitutes the lower peripheral edge of the oil return hole 50. Further, the upper end of the straightening vane 52 is in contact with the peripheral portion of the upper portion of the oil return hole 50.
  • the straightening plate 52, the outer cylinder portion 13 and the partition plate 51 are integrally molded products.
  • the method of integrally forming the flow straightening plate 52, the outer cylinder portion 13 and the partition plate 51 is not particularly limited, such as the method of joining the flow straightening plate 52, the outer cylinder portion 13 and the partition plate 51 by welding.
  • the flow straightening plate 52, the outer cylinder portion 13 and the partition plate 51 are integrally formed by casting.
  • the low-pressure refrigerant gas sucked from the suction pressure side of the screw rotor 7 flows into the compression chamber 11.
  • the refrigerant gas flowing into the compression chamber 11 is sent to the discharge pressure side of the screw rotor 7 while being compressed in the compression chamber 11.
  • the refrigerant gas compressed to a high pressure is discharged from the opening 10a of the slide valve 10 into the discharge chamber 12 together with the refrigerating machine oil injected into the compression chamber 11.
  • the discharged refrigerant gas and refrigerating machine oil flow into the oil separator 3 from the discharge chamber 12.
  • the refrigerant gas and the refrigerating machine oil that have reached the oil separator 3 flow into the inside of the outer cylinder portion 13 from the inflow port 20 formed in the outer cylinder portion 13. That is, the refrigerant gas and the refrigerating machine oil that have reached the oil separator 3 flow into the oil separation space 16 from the inflow port 20 formed in the outer tubular portion 13.
  • the refrigerant gas and the refrigerating machine oil that have flowed into the outer cylinder portion 13 descend while swirling in the gap between the outer cylinder portion 13 and the inner cylinder portion 14.
  • the refrigerating machine oil having a higher density than the refrigerant gas is blown to the inner peripheral surface of the outer cylinder portion 13 by the centrifugal force, and the refrigerating machine oil and the refrigerant gas are separated.
  • the refrigerating machine oil separated by the swirling flow falls on the inner peripheral surface of the outer tubular portion 13 by its own weight and flows on the partition plate 51 toward the oil return hole 50.
  • the refrigerating machine oil that has reached the oil return hole 50 is pushed out by a part of the refrigerant gas flowing from the inside of the outer cylinder portion 13 to the outside through the oil return hole 50 and flows out of the oil return hole 50 to the outside of the outer cylinder portion 13. Then, the oil is stored in the oil storage section 19.
  • the refrigerating machine oil stored in the oil storage section 19 is returned to the compressor body 2 through a path (not shown) provided in the casing 4, and is supplied to the compression chamber 11 and the bearing 8.
  • the refrigerant gas separated from the refrigerating machine oil descends while swirling and is folded back inward by the partition plate 51 in the folding space 16a.
  • the folded-back refrigerant gas flows into the inner tubular portion 14 as an upward flow while continuing to swirl inside the refrigerant gas before being folded in the oil separation space 16.
  • the refrigerant gas flowing into the inner tubular portion 14 passes through the inner tubular portion 14, passes through the check valve 18 from the outlet portion 15a of the lid portion 15, and flows out of the oil separator 3. That is, the refrigerant gas that has flowed into the inner tubular portion 14 passes through the inner tubular portion 14, passes through the check valve 18 from the outlet portion 15 a of the lid portion 15, and flows out of the screw compressor 1. To do. Further, part of the refrigerant gas that descends while swirling inside the outer tubular portion 13 tries to flow into the oil storage portion 19 from the oil return hole 50 as a swirling flow.
  • the refrigerating machine oil that is roughened and jumped up returns to the inside of the outer tubular section 13, It is wound up by the swirling flow in the tubular portion 13 and flows out of the screw compressor 1. That is, the refrigerating machine oil flows out into a range on the downstream side of the screw compressor 1 in the refrigeration cycle circuit.
  • the straightening plate 52 is provided in the oil return hole 50.
  • the rectifying plate 52 provided in the oil return hole 50 is used. Rectified. Therefore, the oil separator 3 according to the first embodiment can suppress the oil level of the refrigerating machine oil stored in the oil storage portion 19 from being roughened, as compared with the conventional oil separator. Therefore, the oil separator 3 according to the first embodiment has improved oil separation efficiency as compared with the related art.
  • the oil separator 3 according to the first embodiment can suppress the refrigerating machine oil from flowing out of the screw compressor 1 as compared with the conventional case, and is a range on the downstream side of the screw compressor 1 in the refrigeration cycle circuit. It is possible to suppress the outflow of refrigeration oil more than ever before.
  • FIG. 3 is a cross-sectional view showing another example of the oil separator of the screw compressor according to Embodiment 1 of the present invention.
  • FIG. 3 is a diagram in which another example of the oil separator 3 is cut at a position corresponding to the AA cross section of FIG. 1.
  • FIG. 3 when explaining the oil separator 3 shown in FIG. 3, the difference with the oil separator 3 shown in FIG. 1 and FIG. 2 is demonstrated. Items not described when describing the oil separator 3 shown in FIG. 3 are the same as those of the oil separator 3 shown in FIGS. 1 and 2.
  • the oil return hole 50 is provided with a plurality of straightening vanes 52 arranged at predetermined intervals.
  • the oil separation efficiency is further improved as compared with the case where a single straightening vane 52 is provided in the oil return hole 50. Therefore, by providing a plurality of flow straightening plates 52 in the oil return hole 50, it is possible to prevent the refrigerating machine oil from flowing out of the screw compressor 1 as compared with the case where a single flow straightening plate 52 is provided in the oil return hole 50. Further, it is possible to further suppress, and it is possible to further suppress the refrigerating machine oil from flowing out to the range on the downstream side of the screw compressor 1 in the refrigeration cycle circuit.
  • the screw compressor 1 described above was a single screw compressor.
  • the screw compressor 1 provided with the oil separator 3 is not limited to a single screw compressor.
  • a twin screw compressor that includes a pair of screw rotors each having a spiral groove serving as a compression chamber formed on an outer peripheral portion thereof and that combines a pair of screw rotors to compress a refrigerant gas.
  • the screw compressor 1 provided with the oil separator 3 may be, for example, such a twin screw compressor. That is, the screw compressor 1 provided with the oil separator 3 is not limited in compression method as long as the screw compressor 1 includes a screw rotor having a spiral groove serving as a compression chamber formed in the outer peripheral portion.
  • the oil separator 3 is attached to the casing 4 of the compressor body 2 with a bolt.
  • the outer cylinder portion 13 of the oil separator 3 and the casing 4 may be integrally formed. Further, the oil separator 3 may be installed separately from the compressor body 2.
  • the rotation speed of the rotor 5b of the motor 5 is not particularly mentioned.
  • the screw compressor 1 may have a configuration in which the rotor 5b is driven at a constant rotation speed, or may have a configuration in which the rotation speed of the rotor 5b can be changed by an inverter or the like.
  • the refrigerant applied to the screw compressor 1 is not limited to a specific refrigerant. For example, it is preferable to select one having a low GWP in consideration of the influence on the environment.
  • the refrigerant having a low GWP is, for example, R32, HFO-1123, HFO-1234yf, HFO-1234ze, or a mixed refrigerant containing at least one of these.
  • the refrigerant applied to the screw compressor 1 may be a natural refrigerant such as carbon dioxide.
  • the oil separator 3 according to the first embodiment is provided in a tubular outer tubular portion 13 in which the refrigerant gas inlet 20 is formed, and in a position inside the outer tubular portion 13 that faces the inlet 20.
  • a cylindrical inner cylinder part 14, an oil storage part 19 provided below the outer cylinder part 13 for storing refrigerating machine oil, and a partition plate 51 for partitioning the outer cylinder part 13 and the oil storage part 19 are provided.
  • the oil separator 3 according to the first embodiment is formed with an oil return hole 50 that connects the inside of the outer cylinder portion 13 and the oil storage portion 19 to each other.
  • the oil return hole 50 is provided with the flow straightening plate 52.
  • the oil separator 3 according to the first embodiment configured as described above, when the swirling flow inside the outer tubular portion 13 enters the oil storage portion 19 from the oil return hole 50, the oil separator 3 is provided in the oil return hole 50.
  • the straightening plate 52 is straightened. Therefore, the oil separator 3 according to the first embodiment can suppress the oil level of the refrigerating machine oil stored in the oil storage portion 19 from being roughened, as compared with the conventional oil separator. Therefore, the oil separator 3 according to the first embodiment has improved oil separation efficiency as compared with the related art.
  • the oil separator 3 according to the first embodiment can suppress the refrigerating machine oil from flowing out of the screw compressor 1 as compared with the conventional case, and is a range on the downstream side of the screw compressor 1 in the refrigeration cycle circuit. It is possible to suppress the outflow of refrigeration oil more than ever before.
  • the oil return hole 50 is formed on the side surface of the outer tubular portion 13.
  • the flow direction of the refrigerant gas flowing from the oil return hole 50 into the oil storage portion 19 is determined by the oil level of the refrigerating machine oil stored in the oil storage portion 19. The direction is almost parallel to. Therefore, by forming the oil return hole 50 on the side surface of the outer tubular portion 13, it is possible to further suppress the oil surface of the refrigerating machine oil stored in the oil storage portion 19 from becoming rough, and to further improve the oil separation efficiency. You can
  • the end portion of the straightening vane 52 is in contact with the peripheral portion of the oil return hole 50.
  • the current plate 52, the outer cylinder portion 13 and the partition plate 51 are integrally molded products.
  • the rectifying plate 52, the outer cylinder portion 13 and the partition plate 51 are integrally molded products.
  • the current plate 52, the outer cylinder portion 13 and the partition plate 51 are integrally formed by casting.
  • the outer cylinder portion 13 and the partition plate 51 are formed as an integrally molded product, if the integrally molded product is manufactured by casting, the manufacturing of the integrally molded product becomes easy. Thereby, the oil separator 3 can be manufactured more inexpensively.
  • the screw compressor 1 according to the first embodiment the oil separator 3 according to the first embodiment and the spiral groove 7a serving as the compression chamber 11 for compressing the refrigerant gas are formed in the outer peripheral portion. And a screw rotor 7. Therefore, the screw compressor 1 according to the first embodiment can have the same effect as the oil separator 3 according to the first embodiment.
  • Embodiment 2 In the second embodiment, an example of a refrigeration cycle device including the screw compressor 1 shown in the first embodiment will be described.
  • FIG. 4 is a refrigerant circuit diagram showing a refrigeration cycle device according to Embodiment 2 of the present invention.
  • the refrigeration cycle device 200 includes a screw compressor 1, a condenser 201, an expansion valve 202 and an evaporator 203.
  • the screw compressor 1, the condenser 201, the expansion valve 202 and the evaporator 203 are connected by a refrigerant pipe to form a refrigeration cycle circuit. Then, the low-pressure refrigerant gas flowing out from the evaporator 203 is sucked into the screw compressor 1 and becomes high-temperature and high-pressure refrigerant gas.
  • the high-temperature high-pressure refrigerant gas is condensed in the condenser 201 to become a high-pressure liquid refrigerant.
  • This liquid refrigerant is decompressed and expanded by the expansion valve 202 to become a low-temperature low-pressure gas-liquid two-phase refrigerant.
  • This gas-liquid two-phase refrigerant is evaporated in the evaporator 203 to become low-pressure refrigerant gas.
  • the screw compressor 1 described in the first embodiment can be applied to such a refrigeration cycle device 200, for example.
  • the refrigeration cycle apparatus 200 can be used as an air conditioner, a refrigeration apparatus, a water heater, or the like.
  • the refrigeration cycle apparatus 200 according to the second embodiment includes the screw compressor 1 shown in the first embodiment, a condenser 201, an expansion valve 202 and an evaporator 203.
  • the screw compressor 1 shown in the first embodiment can suppress refrigerating machine oil from flowing out of the screw compressor 1 more than before. Therefore, the refrigeration cycle apparatus 200 according to the second embodiment including the screw compressor 1 shown in the first embodiment is in a range from the screw compressor 1 to the downstream side of the screw compressor 1 in the refrigeration cycle circuit. Outflow of refrigerating machine oil can be suppressed more than ever before. Therefore, the refrigeration cycle apparatus 200 according to the second embodiment can suppress deterioration in heat exchange performance of the condenser and the evaporator due to the refrigeration oil as compared with the related art, and is a refrigeration cycle apparatus with higher performance than the related art.

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  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

Ce séparateur d'huile comprend : une partie cylindrique exterieure dans laquelle un orifice d'entrée pour un gaz réfrigérant est formé; une partie cylindrique interieure disposée dans une position faisant face à l'orifice d'entrée à l'intérieur de la partie cylindre externe; un réservoir d'huile qui est disposé au-dessous de la partie de cylindre exterieur et qui stocke l'huile de machine frigorifique; et une plaque de séparation qui sépare la partie de cylindre exterieur et le réservoir d'huile. Un trou de retour d'huile est formé qui communique entre l'intérieur de la partie cylindrique exterieure et le réservoir d'huile, et une plaque de rectification est disposée sur le trou de retour d'huile.
PCT/JP2018/048176 2018-12-27 2018-12-27 Séparateur d'huile, compresseur à vis et dispositif à cycle frigorifique WO2020136815A1 (fr)

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PCT/JP2018/048176 WO2020136815A1 (fr) 2018-12-27 2018-12-27 Séparateur d'huile, compresseur à vis et dispositif à cycle frigorifique

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PCT/JP2018/048176 WO2020136815A1 (fr) 2018-12-27 2018-12-27 Séparateur d'huile, compresseur à vis et dispositif à cycle frigorifique

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Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003201964A (ja) * 2002-01-09 2003-07-18 Seiko Instruments Inc 気体圧縮機
JP2009024534A (ja) * 2007-07-18 2009-02-05 Daikin Ind Ltd 冷凍装置
JP2014211101A (ja) * 2013-04-18 2014-11-13 三菱電機株式会社 圧縮機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2003201964A (ja) * 2002-01-09 2003-07-18 Seiko Instruments Inc 気体圧縮機
JP2009024534A (ja) * 2007-07-18 2009-02-05 Daikin Ind Ltd 冷凍装置
JP2014211101A (ja) * 2013-04-18 2014-11-13 三菱電機株式会社 圧縮機

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